JPH0361047B2 - - Google Patents

Description

Claim 1: In a bearing method for a hydrostatic or aerostatic bearing, at least one ring-shaped seal ring supported by a stationary first bearing body is slidable relative to the first bearing body. A second bearing surface with a
One end surface facing the bearing body is in line contact with the second bearing body, and the other seal ring has one end surface facing the second bearing body in line contact with the second bearing body, and the seal ring is in line contact with the second bearing body. A bearing method characterized in that a plane passing through a contact surface of the second bearing body occupies an angular position with respect to the axis of symmetry of the second bearing body, and a pressure fluid is supplied between both seal rings.

2. A first bearing body that is stationary, a second bearing body that has a bearing surface that is slidable with respect to the first bearing body, a space between the two bearing bodies that has a fluid inside, and this space. a first member disposed on the first bearing body for sealing and movable in a direction away from the bearing surface and spaced apart from the bearing surface;
an end face and a second end face facing the second bearing body, the second end face having at least a pair of seal rings having a linear annular contact surface;
A bearing device characterized in that one of the seal rings is configured such that a plane passing through a contact surface of the seal ring occupies an angular position with respect to the axis of symmetry of the second bearing body.

3. The seal ring engages with the first end surface and is provided within the first bearing body, pressurizes the first end surface so as to be in line contact with the bearing surface only along the annular contact surface, and closes the space. 3. A device as claimed in claim 2, including a spring adapted to seal.

4. The device of claim 3, wherein the first bearing body has a chamber for accommodating the seal ring and the spring, the chamber following the shape of the seal ring.

5. Apparatus according to claim 4, wherein the sealing ring has opposing envelope surfaces and is guided by the surfaces of the chamber in cooperation with the envelope surfaces.

6. The device of claim 3, wherein the chamber is annular and the second bearing body is an axis.

7. The device of claim 3, wherein the chamber is annular and the second bearing body is a disc-shaped body.

Description The present invention relates to a bearing method and apparatus for a hydrostatic or aerostatic bearing that receives fluid and performs a bearing action.

The main object of the invention is to provide a method and a device as described above for generating forces acting on bearings in a specified direction, and by such a method it is possible to use expensive roller bearings, for example in axially reciprocating engines. The need to use is reduced. It would also be desirable to be able to combine different types of bearings with hydrostatic or aerostatic bearings, so as to prolong the service life in terms of working reliability at high speeds and at the same time during bearing operation. It is possible to provide bearing devices of small size in carefully defined locations where they are mounted.

The above-mentioned objects are achieved by the method and device of the present invention, which provides a bearing method for a hydrostatic or aerostatic bearing, in which the bearing body is supported by a stationary first bearing body and is ring-shaped. At least one seal ring has a bearing surface that is slidable relative to the first bearing body, and one end surface facing the second bearing body is in line contact with the second bearing body, and the other seal rings are in line contact with the second bearing body. , one end surface facing the second bearing body is in line contact with the second bearing body, and a plane passing through the contact surface of the seal ring occupies an angular position with respect to the symmetry axis of the second bearing body. , is characterized in that pressure fluid is supplied between both seal rings.

Furthermore, the present invention provides a stationary first bearing body, a second bearing body having a bearing surface that is slidable with respect to the first bearing body, and a gap between the two bearing bodies having a fluid therein. space, and a first end surface provided on the first bearing body to seal this space, movable in a direction away from the bearing surface, and spaced apart from the bearing surface, and a second end surface facing the second bearing body. and at least a pair of seal rings, the second end surface of which has a linear annular contact surface, one of the seal rings has a plane passing through the contact surface of the seal ring, and the second end surface has a linear annular contact surface. It is characterized in that it occupies an angular position with respect to the axis of symmetry of the bearing body.

The invention will be described below in conjunction with the accompanying drawings.

1 shows a hydrostatic axial bearing, FIG. 2 shows a hydrostatic shaft bearing used in combination with an axial bearing used in a hydraulic machine with a spherical piston, and FIG. Figure 4 shows a hydrostatic radial bearing for varying the forces acting on the bearing, Figure 4 shows a self-aligning bearing structure for a hydrostatic bearing, and Figure 5 shows a flat bearing surface. 6 shows a schematic cross-sectional view of a hydrostatic bearing with a bearing seal ring, FIG. 6 shows a cross-sectional view similar to FIG. 5 with a bearing seal ring bearing on a concave bearing surface, and FIG. 5 shows a cross-sectional view similar to FIG. 5 with a sealing ring supported on a convex bearing surface and viewed from the force direction; FIG. 8 shows the invention applied to a piston made of a hollow workpiece; FIG. 9 The figures show the invention applied to a rotating piston; Figures 10 to 12 show a linear seal of a seal ring to a moving bearing body with a flat bearing surface, a concave bearing surface and a convex bearing surface, respectively; 13 shows the invention applied to a rotating vertical shaft having a flange and a sealing ring supported concentrically on the shaft; FIG. 14 shows the bearings in contact; FIG. 14 shows the bearing eccentrically supported on the shaft; FIG. 15 shows a pressure distribution diagram in a hydrostatic bearing with a sealing ring supported on a flat bearing surface; FIG. 16 shows an arrangement similar to FIG. 17 shows a pressure distribution diagram in a hydrostatic bearing with a sealing ring supported on a concave bearing surface, FIG. 17 shows a diagram of the angular relationship in a sealing ring supported on a shaft, and FIG. 19 shows a diagram of the angular relationship in the sealing ring cooperating with the cavity, FIG. 19 shows a sectional view of a known hydraulic pump/drive source with roller bearings, and FIG. 20 applies to the hydraulic pump/drive source. FIG. 21 shows a detailed view of the arrangement of a seal ring provided in the hydraulic pump/drive source shown in FIG. 20, for example, and FIG. 23 shows a force distribution diagram of a seal ring arranged according to the invention, FIG. 24 shows a shaft seal, and FIG. 25 shows a convex spherical bearing surface. 26 to 28 show the invention applied to a supporting stationary bearing pocket with seals cooperating with a supporting movable load bearing body; FIGS. 26-28 show two seals, one inside the other; 29 shows a bearing with three sealing rings internal to each other; FIGS. 30-32; FIG. FIG. 3 is a diagram showing different embodiments of the wire seal ring ends of each seal ring.

The invention described below and illustrated in the accompanying drawings comprises:
Although referring to bearings of the hydrostatic or aerostatic type, only hydrostatic bearings will be discussed below for convenience.

The vertical bearing shaft 1 shown in FIG. 1 is fitted into a bearing housing 2 corresponding to the shape of this shaft, supporting a load not shown and forming the "second" bearing body of the bearing. There is. On the other hand, the bearing housing 2 forms a "first" bearing body. Two ring-shaped recesses 3, 4 are provided in the bearing housing 2, one of which extends perpendicularly to the bearing shaft 1 and the central axis 5 of the housing 2, and the other ring-shaped recess 3 extends perpendicularly to the bearing shaft 1 and the central axis 5 of the housing 2. The groove 4 is centered on this central axis 5.
is located at an angular position relative to the The seal rings 6 and 7 for the recesses 3 and 4 are respectively accommodated in one of the recesses 3 and 4, and the one side portions 6A and 7A of the seal rings 6 and 7 are respectively located in the recesses (grooves) 3 and 4. Bearing contact abutment can be made with appropriate sides 3A, 3B of 4. The sealing rings 6, 7 are preferably split or integral rings of elastic material, for example made of high-speed steel, hard metals, composite materials, etc., each having an inclined contact surface 6B on its inner envelope surface. , 7B. The two contact surfaces 6B, 7B perform a bearing action along the periphery of the shaft 1 at their inner facing contact surface ends.

Pressurized liquid is supplied into the space 9 via a passage 8 communicating with the space 9 formed between the two sealing rings 6,7. The rotation of the shaft 1 relative to the bearing housing 2 and the pressurized liquid in the bearing space 9 generate a pressurizing force that acts on the bearing in a predetermined direction. In FIG. 1, this pressing force is indicated by an arrow extending away from the centerline 5 of the shaft 1. This directional force component acts as a reaction to other forces on the bearing and can reduce or change the main force, making it possible, for example, to combine hydrostatic bearings with other types of bearings, allowing higher sliding speeds. This makes it possible to operate with large pressure gradients on the bearing. In other words, since there is a risk that the shaft 1 may lose its balance depending on the direction of the external force, if the seal rings 6 and 7 are provided asymmetrically, the internal space 9 will have an irregular shape, and the force can be applied in the desired direction. The pressure of the fluid applied to the interior space 9 will displace the bearing and balance it during rotation.

The wear of the bearing body against the seal ring supported by the contact surfaces 6B, 7B is extremely small since there is only line contact between the seal rings 6, 7 and the bearing surface.

The outer shape of the inclined seal ring 7 along the groove 4 is as follows:
Owing to its oval shape, this seal ring 7 will be able to carry out a bearing action with the seal ring contact surface 7B in close abutment against the periphery of the shaft 1. The other ring 6 with the groove 3 has an approximately circular shape.

The bearing shown in FIG. 2 shows an example of applying a static axial bearing to a hydraulic machine 20 having a spherical piston 21, but of course the piston does not necessarily have to be spherical, but rather cylindrical and articulated. The principle can also be applied to a piston having a piston rod. In a manner similar to the arrangement of the bearings shown in FIG. It is in line contact with 23A. Ring gear 2 forming part of hydraulic machine 20
6, a circular groove 27 is formed in the bearing housing, and a flange 22A projecting from the upper end of the shaft 22 is mounted on the ring gear 26. An upwardly spring-biased seal ring 28 is supported in the groove 27 until it is in line contact with the lower part of the ring gear 26. The pressurized fluid flows through the passage 25A of the bearing housing 25.
It is formed between the two seal rings 23 and 28 and is supplied into the space 29 via the seal ring 23, 28.

The force component generated is indicated by a dotted arrow in FIG. 2, and as is clear from FIG. 2, this component force is in a direction opposite to the force exerted by the piston 21 on the bearing. in this way,
It can be completely mounted on the shaft 22 without any other roller bearings.

FIG. 3 shows a sleeve 31 mounted at a distance from each other and fixed on the shaft 30, which sleeve 31 has two spherical bearing surfaces 31A, 31B with a concave middle; A shaft 30 is horizontally supported by this sleeve 31.
The bearing housing 32, which is formed by two bearing housing parts 32A, 32B that can be connected to each other in the assembled state, forms a fluid-receiving chamber 33 into which the fluid flows through the passage 3.
4. End walls 3 are provided at both ends of the chamber 33.
3A and 33B are formed, and this end wall 33
Seal rings 35, 36 can be supported on one side of side portions 35A, 36A relative to A, 33B, respectively. These end walls 33A, 33B are arranged in such a way that they can assume an angular position, preferably an oblique position, with respect to the axis of symmetry 30A of the axis 30 of the sleeve 31. Two sealing rings 35, 36 with line contact surfaces are connected to respective spherical bearing surfaces 31.
It is supported around A and 31B. In relation to each other two bearing housing parts 32A, 3
By connecting 2B, when the fluid pressure is constant, the force applied to the bearing can change not only its magnitude but also its direction. Only by connecting the two housing parts 32A, 32B as an integral member can the direction of the force on the bearing be changed. An example of this force is indicated by an arrow in FIG.

By arranging it on the shaft instead of in the bearing housing, the ring can be mounted in a similar chamber. At this time, oil or the like can be supplied into the shaft through the passage.

FIG. 4 shows how the present invention may be utilized to support a radially loaded rotating shaft 40 using a spring-loaded seal providing a line sealing action. Possible configurations of self-aligning bearing structures for hydrostatic bearings with rings are shown. A number of bearing members 42 are arranged planetarily around the shaft 40 and are connected via passages 43 to a common pressure source to provide balanced pressure. The illustrated bolt 44 with an adjusting nut 45 continuously normalizes the position of the shaft 40 relative to the bearing body 42, increasing the flow area of the inlet section for pressure balance as the shaft 40 approaches the bearing body 42. increase At this time, the oil pressure increases in the pocket 46 inside the seal ring 41, and the shaft 40 is pulled up until the load on the shaft 40 and the oil pressure inside the seal ring 41 are balanced.

Spring 48 pressing bolt 44 against shaft 40
The lid 47 containing the bolt is removable so that the nut 45 can be adjusted along the bolt.

The illustrated principle makes it possible to determine the center of rotation of the shaft 40 very precisely and to keep it within very small limiting changes even with large changes in the load. In addition, the above-mentioned bearings, thrust bearings, such as propeller thrust bearings, turbine engine thrust bearings, etc., in which a rotating disk has a bearing surface and a number of bearing bodies each having a seal ring operate against this disk. Other types of self-centering bearing structures can also be applied.

A seal ring 50 disposed in a recess 51 in a bearing fixed to a bearing housing 52 is shown in FIG.
3, the sealing ring 50 is spring-loaded against a loaded movable body 54 having a substantially flat bearing surface 55. Oil can be supplied to the bearing via a passageway 56 in the bearing housing 52, which passageway is connected to the recess 5.
It communicates with the center of the seal ring in 1. Also, this seal ring 50, like the other rings shown in other drawings, supports the bearing surface it has in a line contact surface.

A structure similar to that shown in FIG. 5 is shown in FIGS. 6-7, except that the movable body 60 under load is shown in FIGS. , 70 have a concave bearing surface 61 and a convex bearing surface 71.

FIG. 8 shows how one end of a piston 81 with an oil supply channel 81 along the central axis is placed in a recess 83 that matches the shape of the seal ring 82, so that the seal ring 82 In the state shown in FIG. 21, a pivoting action can be performed on the bearing surface, forming a bearing with a hydrostatic bearing space.

A rotating piston 90 movably mounted in a bearing body 91 having a cylinder space for the piston 90 has an angular position with respect to the axis of symmetry 94 of the sealing ring 92 in the recess 93, as shown in FIG. are doing.

10 to 12 show a seal ring 10
0, 110, 120 are shown, and each of these seal rings is a bearing body 101, 111, 121.
supported by bearing surfaces 103, 113,
123, the sealing surfaces 102, 11 along this
2,122 line contact bearings.
Therefore, the angle between the perpendicular to the bearing surfaces 103, 113, 123 and the top surface of the seal rings 100, 110, 120 is equal to or greater than 90 degrees.

Figures 13-14 show how the bearing principle is utilized to provide axial forces acting on flanged rotating shafts 130, 140. The seal ring 131 is
It is shown concentrically around the axis 130, with the resulting force acting in the lifting direction at the center of the axis as shown by the arrow. Seal ring 141 shown in FIG.
is located eccentrically relative to the shaft 140, with the resulting force being displaced parallel to the lateral direction of the shaft.

15-16, seal rings 152, 162 are brought into contact with flat or curved bearing surfaces 151, 161, as shown along the diameter of seal rings 152, 162, respectively. The pressure distribution in two bearings 150, 160 is shown.

The two bearings 170 and 180 are the 17th
18 and one of the bearings shows a sealing ring 172 cooperating with the outer part of the shaft 171 and the other one cooperating with the inner surface 181 of the bearing housing 182. 183 is shown. In the figure, the appropriate angular position is shown and the law is valid such that angle γ is greater than angle O to create a bearing in line contact between the sealing ring and the bearing surface that can cooperate with it.

FIG. 19 shows a cross-sectional view of a drive source of a hydraulic pump 190 in which the bearing is a roller bearing.

FIG. 20 shows how bearings in a drive source similar to that shown in FIG. 19 are partially replaced by bearings according to the invention, hydrostatic bearings 201, 202. ing.

The piston 212 and the bearings 210, 211 of the pivoting flange 213 of such a drive source are the 21st
It is shown as an enlarged view in the figure.

Sliding ferrule 220 and seal ring 22
A piston 222 having a number 1 is shown in FIG.

The force balance in a seal ring 231 made in accordance with the present invention is shown in FIG. .

A sealing ring 240, which has a somewhat different cross-section than the other rings shown, bears a line contact surface 241 against the bearing surface of a bearing part 244 supported on an axle 243 and between a bearing space 245 and the surrounding air. It is sealed.

FIG. 25 shows the application of the invention to a supporting fixed bearing pocket 251 having a sealing ring 250 and cooperating with a loaded movable bearing body 252 supporting a projecting spherical bearing surface 253. There is.

In the embodiments shown in FIGS. 26 to 29, it is shown how two or more sealing rings are arranged inside each other concentrically to improve the sealing effect of the bearing. There is.

In FIG. 26, two seal rings 260 and 261 are arranged concentrically on the bearing surface 26, respectively.
3 shows how it is supported by the bearing body 262 for bearing against the bearing body 262.

Another arrangement of sealing rings is shown in FIG. 27 with two sealing rings 270, 271, which have different heights, are supported by a common bearing body 272, and have a bearing surface 273. We are trying to be supported by this. By arranging it in this way, the usable space can be made smaller than in the arrangement described above.

The arrangement of the two seal rings 280, 281 is shown in FIG. 28, in which the inner seal ring 280 has a contact surface 280A at its outer diameter, and the outer seal ring 28
1 has a contact surface 281A at its inner diameter. The ring-shaped space 282 between the two seal rings 280 and 281 communicates with the top side of the bearing body 284 through a passage 283.
is used to adjust the pressure between rings 280 and 281. A passageway 285 communicates with the space 286 in which an inner ring 280 is received and supported. The two rings 280, 281 have their contact surfaces 280, respectively, against the bearing surface 287.
It is supported by A, 281A.

Figure 29 shows three seal rings 290, 29.
1,292 arrangement is shown, with two ring-shaped spaces 293, 294 formed between seal rings 290, 291 and 291, 292, each space having a passageway 2 extending in the bearing body 297.
95 and 296 are provided, respectively. Additionally, an additional passageway 299 is provided in communication with the space 290, and an inner ring 290 is received and supported on the outside of the bearing body. Passage 295, 29
6,299 are two ring-shaped spaces 293, 294 in which the inner ring 290 is received and supported.
and the pressure within the space 290 are individually adjusted and shown. All seal rings are preferably arranged to bear against a common bearing surface 298.

FIG. 30 shows a seal ring having a contact surface 300A at its outer diameter 300B. The cylindrical outer diameter 300B of this ring 300 must closely fit into a corresponding recess in the bearing body. The ring 300 thus illustrated is axially balanced.

Further shown in FIG. 31 is another seal ring 310, which defines a contact surface 310A at its inner diameter 310B. The cylindrical inner diameter 310B of this seal ring 310 must closely fit into a corresponding recess in the bearing body. The seal ring 310 thus illustrated is also axially balanced.

In the illustrated seal ring 320 of FIG. 32, the contact surface 320A is somewhat recessed. Therefore, this seal ring 320 is not completely axially balanced. Seal ring 310 in FIG. 31 can be constructed in a similar manner with a contact surface having a diameter somewhat larger than that corresponding to its inner diameter. This seal ring is also not perfectly axially balanced.

The features of the invention are clear from the above description taken together with the accompanying drawings. The idea of the invention is that it is important that the sealing ring provides a force acting in a predetermined direction. This force is proportional to the current oil pressure, inclination, and ring shaft diameter.

In addition to the above-mentioned inventive advantages obtained by the present invention, the bearing is less sensitive to impurities among other things for any narrow passages. This passage is clogged with impurities which are not needed in the bearing according to the invention. Furthermore, the bearing of the present invention is mechanically superior to conventional bearings, and has sufficient mechanical strength against high-speed rotation and load. The narrow seal ring surface of the seal ring allows the bearing to obtain a good cooling effect, and high-speed sliding allows safe work with sufficient load.

The invention is not limited to what has been described above in conjunction with the accompanying drawings, but may vary within the scope of the claims.